• 专利附录
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    • 专利摘要:
    The invention relates to a torque transmission device (10), in particular for a motor vehicle, comprising a torque input element (12, 16a, 16b) intended to be coupled to a crankshaft and comprising first and second washers. guide (16a, 16b), an annular web (24), a torque output member including a hub (14) for coupling to an input shaft of a gearbox, the web (24) being adapted to slide along its axis (X) relative to the hub (14), a primary damper (A1) arranged between the torque input member (12, 16a, 16b) and the web (24) and a secondary damper or pre-damper arranged between the web (24) and the torque output member (14), friction means capable of generating a hysteresis torque during rotation of the web (24) with respect to the element torque input (12, 16a, 16b).
    公开号:FR3041402A1
    申请号:FR1558813
    申请日:2015-09-18
    公开日:2017-03-24
    发明作者:Dominique Dael
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    Torque transmission device, in particular for a motor vehicle
    The present invention relates to a torque transmission device belonging for example to a clutch device, such as a friction clutch, in particular for a motor vehicle.
    The document FR 2 918 432 discloses a torque transmission device, in particular for a motor vehicle, comprising a torque input element intended to be coupled to a crankshaft and comprising a first and a second guide ring, an annular web, a torque output member comprising a hub to be coupled to an input shaft of a gearbox, the sail being slidable along its axis relative to the hub. The device further comprises a primary damper arranged between the torque input member and the web and a secondary damper or pre-damper arranged between the web and the torque output member. Friction means make it possible to generate a hysteresis torque during the rotation of the web with respect to the torque input element, said friction means comprising an application washer mounted axially between the web and the first washer of guiding, at least one elastic member capable of exerting an axial force and mounted axially between the application washer and the first guide washer, and a variable hysteresis washer mounted axially between the second guide washer and the web, the elastic member tending to push the application washer and the web towards the variable hysteresis washer so that said variable hysteresis washer generates a hysteresis torque by friction. The variable hysteresis washer and the application washer are rotatably coupled to each other.
    The variable hysteresis washer is formed from a sheet and comprises wedge-shaped edges, folded axially and forming stops capable of cooperating with complementary stops of the web, so as to perform a coupling in rotation of the web, of the variable hysteresis washer and the application washer, when the deflection of the web relative to the torque entry element exceeds a specific angular range and so as to decouple the web, on the one hand, and the variable hysteresis washer and the application washer, on the other hand, when said deflection is situated in said determined angular range.
    The flanges are particularly fragile and the hysteresis washer is relatively difficult to achieve by stamping, because of the presence of said flanges. The invention aims to remedy these disadvantages in a simple, effective and economical way. For this purpose, the invention relates to a torque transmission device, in particular for a motor vehicle, comprising a torque input element intended to be coupled to a crankshaft and comprising a first and a second guide ring, an annular sail. , a torque output element comprising a hub intended to be coupled to an input shaft of a gearbox, the sail being able to slide along its axis with respect to the hub, a primary damper arranged between the element of torque entry and the web and a secondary damper or pre-damper arranged between the web and the torque output member, friction means capable of generating a hysteresis torque during the rotation of the web relative to the torque input element, said friction means comprising an application washer axially mounted between the web and the first guide washer, a hysteric washer variable sis mounted axially between the second guide washer and the web, at least one resilient member tending to push the application washer and / or the web towards the variable hysteresis washer so that said washer variable hysteresis generates a hysteresis torque by friction, the variable hysteresis washer and the application washer being rotatably coupled to each other, characterized in that the pre-damper comprises at least one coupled auxiliary guide washer in rotation with the web, said auxiliary guide washer comprising a stop adapted to cooperate with a complementary abutment of the application washer so as to perform a coupling in rotation of the web, the variable hysteresis washer and the washer application, when the deflection of the web relative to the torque input member exceeds a determined angular range and so as to decouple the web, on the one hand, and the variable hysteresis washer and the application washer, on the other hand, when said deflection is located in said determined angular range. The invention thus proposes an alternative structure for coupling in rotation the variable hysteresis washer and the application washer to the web, beyond the determined angular range. This new structure does not involve a hysteresis washer with wedge-shaped edges, making the proposed solution less fragile and more easily achievable than in the prior art, without the need for additional elements.
    The device according to the invention may also comprise one or more of the following features: the pre-damper comprises a first and a second auxiliary guide washer coupled in rotation with the annular web, an auxiliary annular web mounted axially between the washers auxiliary guide means and adapted to be coupled in rotation with the torque output member, and at least one resilient member mounted between the auxiliary guide washers and the auxiliary web and adapted to oppose the rotation of the auxiliary guide washers relative to the auxiliary web, the device comprises a first bearing rotatably coupled to the first guide washer and a second bearing rotatably coupled to the second guide washer, the hub being held in abutment and recentered between the first and second bearings the hub is held in abutment against the first bearing and against the second bearing by at least one first spring washer, mounted between one of the guide washers and one of said bearings, and adapted to exert an axial force tending to press said bearing on the hub, the device comprises a second elastic washer arranged axially between the guide washers and the application washer, adapted to exert an axial force on the applicator washer, the first and second guide washers are pivotally mounted around the hub, via the first and second bearings, the first and second bearings are made of plastic material, possibly reinforced with fibers, the application washer is made of plastic material, possibly reinforced with fibers, the application washer comprises housings in which are engaged, with a set angular, pads of at least one guide ring of the pre-damper, so as to form the complementary stops, - the washer of Pplication comprises recesses of which at least one comprises snap-fit means in the form of hooks or lugs, the application washer comprises an annular friction surface, extending for example radially, turned towards the first guide washer and opposite the variable hysteresis washer, - the second elastic washer is mounted in abutment between the first guide ring of the primary damper and the radial surface of the application washer, - the second elastic washer is preferably spring steel and is secured in rotation with the first guide ring of the primary damper, for example by cooperation of tabs and complementary notches, - the annular friction surface comprises a metal part, for example a metal annular insert , fixed with respect to the application washer, - the variable hysteresis washer is made by example from a metal sheet, and comprises a substantially radial annular portion, from which eight lugs extend axially towards the applicator washer and from which four lugs extend radially outwardly. - Some of said tabs have notches and are engaged in the recesses of the application washer so that hooks or lugs of the aforementioned latching means are snapped into said notches, - a bearing washer, performed for example metal, is interposed axially between the variable hysteresis washer, more particularly its annular portion, and the inner periphery of the annular web, - the support washer is rotatably secured to the second guide ring, by intermediate of legs of the support washer which are mounted in complementary shaped lights of the second washer of guidance, - a third elastic washer is mounted in abutment between the first guide ring of the primary damper and a guide ring of the pre-damper, - the third spring washer is secured in rotation with the first guide ring of the primary damper, for example by cooperation of radial tabs and complementary notches, - the device comprises a first and a second friction washers adapted to be coupled in rotation with the auxiliary web of the pre-damper, - the first friction washer is preferably made of steel and comprises a radial annular portion from which tabs extend axially and are engaged in notches of the auxiliary web of the pre-damper, so as to be able to rotate the first friction washer and the web auxiliary, - the annular portion of the first friction ring has notches at the outer periphery. the second friction washer is made of plastic, possibly reinforced with fibers, the second friction washer comprises a radial annular portion from which studs extend axially so as to engage in the notches of the first friction washer so as to couple in rotation the first and second friction washers, - a fourth elastic washer is mounted in abutment between the first guide ring of the primary damper and the second friction washer, - the fourth spring washer is secured in rotation with the first guide ring, for example by cooperation of radial tabs and complementary notches, - the primary damper comprises, on the one hand, damping means with immediate activation, which are activated as soon as it starts. the angular displacement between the guide washers and the web, and, secondly, the means s of conditional activation damping, which are activated here when the angular displacement between the guide washers and the web exceeds a predetermined threshold angle from a rest position, said threshold angle of the primary damper, damping means of the primary damper comprise circumferentially acting elastic members, such as helical springs, housed in windows of the guide washers and in windows of the annular web; elastic members of a first group, said elastic members with immediate activation, housed without circumferential clearance in the windows of the guide washers and in the windows of the annular web, the conditional activation damping means comprise elastic members of a second group, so-called elastic members with conditional activation, housed without circumferential clearance in the windows of the guide washers and with a predetermined circumferential clearance in the windows of the annular web, the elastic members belonging to the conditional activation damping means are housed with clearance between the tabs extending radially outwardly of the variable hysteresis washer, - the torque input element comprises a friction disc, - the torque transmission device belongs to a clutch device, such as for example a friction clutch, in particular for a motor vehicle the hub is made of metal, the hub comprises axially extending internal splines, able to be coupled to complementary splines of an input shaft of a gearbox, the guide washers are metal, - the guide washers are rotatably coupled to one another by means of small columns, - the friction disc is fixed on one of the guide washers by means of rivets, - the friction disk comprises an annular support whose radially inner periphery is fixed to one of the guide washers, and annular fittings mounted on both sides. other of the support, said gaskets being fixed to the support, for example by means of rivets, - the annular web is made of metal, - the annular web comprises, at the radially inner periphery, a toothing which meshes with a determined circumferential clearance , with a corresponding external toothing of the hub, the internal toothing of the sail forms substantially radial projections intended to cooperate with external complementary recesses of the hub so as to effect a meshing, the pre-damper comprises elastic members, such as, for example straight compression springs, - the auxiliary guide washers of the pre-damper are made of plastic era, optionally reinforced with fibers, - the auxiliary web of the pre-damper comprises, at its radially inner periphery, rotation coupling means adapted to cooperate with the hub, for example with an external groove of the hub, so as to ensure a coupling in rotation, - the first bearing is secured in rotation with one of the guide washers by means of axial fingers cooperating by snapping with a notched internal contour complementary to said guide washer, - the first bearing comprises a surface radial friction, able to bear against a radial shoulder of the hub, - the second bearing is secured in rotation with one of the guide washers with the fingers cooperating with a notched contour complementary to the second guide ring - The second bearing comprises a frustoconical friction surface adapted to bear against a frustoconical surface of the hub, - each elastic washer. e is an elastically deformable compression washer, capable of exerting an axial force, the device is arranged in such a way that, during a first operating phase, immediate friction is generated between the hub and the first bearing, between the hub and the second bearing, and conditional from a predetermined angular range, between the first friction washer and the first auxiliary guide washer, and between the second friction washer and the fourth elastic washer, the device is arranged so that, during a second operating phase, friction is generated between the hub and the first bearing, between the hub and the second bearing, between the web and the support washer, between the first washer and auxiliary guide and the third elastic washer, and between the second friction washer and the fourth elastic washer, - the device is arranged so during a third operating phase, friction is generated between the hub and the first bearing, between the hub and the second bearing, between the web and the support washer, between the first auxiliary guide washer. and the third elastic washer, between the second friction washer and the fourth elastic washer, between the variable hysteresis washer and the second guide washer, between the variable hysteresis washer and the support washer, and between the washer application and the second elastic washer. The invention will be better understood and other details, features and advantages of the invention will become apparent on reading the following description given by way of non-limiting example with reference to the accompanying drawings, in which: FIG. 1 is a view in axial section of the device according to one embodiment of the invention, - Figure 2 is an exploded view, in perspective, of the device; - Figure 3 is a front view, with partial tearing, of a part of the device; FIG. 4 is a front view of a portion of the device; FIG. 5 is an exploded perspective view of a portion of the device; FIG. 6 is an axial sectional view of a portion of the device; FIG. 7 is an exploded perspective view of a portion of the device; FIG. 8 is a front view of a portion of the device; FIG. 9 is an exploded view in perspective and with partial tearing off of part of the device, FIGS. 10 and 11 are perspective views of the application washer and the variable hysteresis washer; FIG. 12 is a perspective view showing the assembly of the application washer and the hysteresis washer; FIG. 13 is a perspective view and with partial tearing of part of the device, FIG. 14 is a perspective view of the pre-damper of the device, FIG. 15 is a front view of a FIG. part of the device, - Figure 16 is a perspective view of the application washer.
    Figures 1 and 2 show a torque transmission device 10 belonging to a clutch device 10, such as a friction clutch, in particular for a motor vehicle. This extends along an axis X and is intended to transmit a torque between a flywheel integral with a driving shaft (not shown), such as for example a crankshaft of an internal combustion engine, and a shaft led (not shown), such as an input shaft of a gearbox.
    The clutch device 1 comprises a primary damper A1 and a secondary damper A2, also called pre-damper, the two dampers being arranged in series between a friction disk 12, intended to be coupled in rotation to the drive shaft, and a radially inner hub 14, intended to be coupled to the driven shaft.
    More particularly, the friction disc 12 is intended to be clamped between the flywheel and a movable pressure plate (not shown). The hub 14 has internal grooves 15i extending axially, able to be coupled to complementary grooves of the driven shaft. The primary damper comprises first and second guide washers 16a, 16b, rotatably coupled by means of columns 17. The guide washers 16a, 16b are pivotally mounted around the hub, by means of annular bearings 18, 20. The friction disk 12 is fixed on the first guide ring by means of rivets 22.
    An annular web 24 is interposed axially between the two guide rings. The annular web comprises, at the radially inner periphery, a toothing 23 which meshes, with a circumferential clearance J1 determined (FIG. 3), with a corresponding external toothing 15e of the outer periphery of the hub 14. More particularly, the internal toothing 23 of the veil 24 forms substantially radial projections intended to cooperate with external complementary recesses of the hub so as to perform a meshing. The primary damper A1 comprises, on the one hand, damping means 25a with immediate activation, which are activated as soon as the angular displacement between the guide washers 16a, 16b and the web 24 begins, and, on the other hand, on the one hand, so-called conditional activation damping means 25b, which are activated here when the angular displacement between the guide washers 16a, 16b and the annular web 24 exceeds a predetermined threshold angle from a rest position, said angle threshold of the primary shock absorber A1.
    The damping means 25a, 25b comprise elastic members with circumferential action, such as helical springs 26a, 26b, 28a, 28b of high stiffness, housed in windows 30 of the guide washers 16a, 16b and in windows 32a and 32a. 32b of the annular web 24. The resilient members 26a, 26b, 28a, 28b are divided into two groups.
    The immediately-activated damping means 25a comprise elastic members 26a, 26b of a first group, called immediate-acting elastic members, housed without circumferential clearance in the windows 30 of the guide washers 16a, 16b and in the windows 32a of the annular sail 24. They participate in the transmission of a rotational torque between the guide washers 16a, 16b and the web 24 from the beginning of a relative rotation between the friction disc 12 fixed on the first guide washer 16a of the damper A1 and the hub 14.
    The conditional activation damping means 25b comprise elastic members 28a, 28b of a second group, called conditional activation elastic members, housed without circumferential clearance in the windows 30 of the guide washers 16a, 16b and with a predetermined circumferential clearance in the windows 32b of the annular web 24. The elastic members 28a, 28b of the second group are here activated in an offset manner to ensure the transmission of a torque that when the angular displacement between the guide rings 16a, 16b and the veil annular 24 exceeds the threshold angle of the primary damper A1. It will be noted that this threshold angle corresponds to the circumferential clearance between the elastic members 28a, 28b and the corresponding windows 32b of the web 24.
    Thus the elastic members 26a, 26b of the first group are activated immediately to transmit the torque permanently, while the elastic members 28a, 28b of the second group are conditionally activated to transmit the torque only when the angular movement between the washers. 16a, 16b and the annular web 24 is here greater than the threshold angle of the primary damper A1. The secondary damper or pre-damper A2 connects the annular web 24 of the primary damper A1 and the hub 14.
    The pre-damper A2 comprises first 34a and second 34b guide washers. These guide washers 34a, 34b are secured in rotation with each other by means of tabs 36a and 36b and all of these two guide washers are hooked on the web 24 by means of axial tabs 39 formed at the periphery. outer of the second guide ring 34b. More particularly, the outer periphery of the first guide ring 34a has pads 35a extending radially outwardly and the outer periphery of the second guide ring 34b has pads 35b extending radially outwardly. The pads 35a alternately comprise tabs 36a and recesses 38a whereas the pads 35b alternately comprise tabs 36b and recesses 38b. The recesses 38a, 38b and the tabs 36a, 36b are positioned in such a way that the tabs 36a are engaged and maintained by clamping or force-fitting in the recesses 38b of the pads 35b of the second washer 34b and that the tabs 36b are engaged and held by clamping or force-fitting in the recesses 38a of the pads 35a of the first washer 34a.
    The second guide ring 34b further comprises tabs 39 extending axially from the radially outer periphery of said washer 34b, in the direction of the annular web 24, opposite the first guide ring 34a. Each tab 39 is engaged and clamped in a notch 40 formed in the radially inner edge of the openings 32a, 32b of the annular web, so as to secure the first 34a and second 34b guide washers to the web 24 of the primary damper A1. In the embodiment shown, the guide washers 34a, 34b are preferably made of plastic, which is optionally reinforced with fibers.
    An auxiliary annular web 42 of the pre-damper A2 is interposed axially between the two guide rings 34a, 34b, co-axially thereto. This auxiliary web 42 is integral in rotation with the hub 14, for example by meshing without play with the external peripheral gearing 15e of this hub 14. The pre-damper A2 also comprises damping means 43 for damping vibrations coming from the motor and also transmit the weak couples.
    The damping means 43 of the pre-damper A2 are of the immediate activation type, that is to say they are activated as soon as the angular displacement between the guide washers 34a, 34b and the web 42 of the pre-damper A2 starts. . According to a variant not shown, the damping means 43 of the pre-damper A2 can also comprise means 43b activation damping, called conditional, which are activated when the angular displacement between the guide rings 34a, 34b and the veil ring 42 of the pre-damper A2 exceeds a predetermined threshold angle from a rest position, said pre-shock threshold angle A2.
    The damping means 43 are formed by circumferentially acting elastic members, such as relatively low stiffness compression coil springs, housed without circumferential clearance in windows 48 of the guide washers 34a, 34b and between tabs 50 of the veil. ring 42 (see Figure 5). The damping means 43 thus contribute to the transmission of a rotational torque between the guide washers 34a, 34b and the auxiliary web 42, from the beginning of a relative rotation between these guide washers 34a, 34b and this sail. 42.
    Thus, all of the resilient members 26a, 26b, 28a, 28b, 43 of the primary damper A1 and the pre-damper A2 thus provides three stages of vibration damping and irregularities of torque.
    Indeed, the resilient members 43 of the pre-damper A2 determine a first damping stage. Furthermore, at the end of the stroke of the pre-damper A2, the elastic members 26a, 26b, 28a, 28b of the primary damper A1 determine second and third damping stages as they are mounted without or with circumferential clearance in their corresponding windows.
    The bearing 18 is secured in rotation with the first guide washer 16a of the primary damper A1 by conventional means, for example axial fingers 52 cooperating with a complementary notched internal contour 54 of the guide washer 16a.
    The bearing 20, participating in the centering of the hub 14, is secured in rotation with the guide washer 16b using conventional means, for example fingers 56 cooperating with a complementary notched contour 58 of the guide washer 16b.
    The bearing 18 and a shoulder 59 of the hub 14 form two complementary radial friction surfaces F1 intended to bear against one another. Furthermore, the bearing 20 and the hub 14 have two frustoconical complementary friction surfaces F2 (Figure 1) intended to bear on one another.
    The friction surfaces F1, F2 are elastically biased in mutual contact by a first elastic washer 60 of axial compression bearing between the first guide washer 16a of the primary damper A1 and the bearing 18.
    The spring washer 60, preferably spring steel, is provided with notches cooperating with the fingers 52 of the bearing 18 so as to perform a coupling in rotation, said lugs 52 also being secured in rotation with the first guide washer 16a.
    In the embodiment shown, the bearings 18 and 20 are made of plastic, possibly reinforced with fibers, and preferably exert a relatively "soft" friction on the hub 14.
    The device further comprises a so-called application washer 63, a variable hysteresis friction washer 64 and a second elastic washer 66.
    The application washer 63 is made for example of plastic material, possibly reinforced with fibers. Said washer 63 comprises housings 70, here four in number, in which are engaged, with an angular play, the pads 35a of the first guide ring 34a of the pre-damper A2, as can be seen in FIGS. 3.
    The angular clearance is for example between 2 ° and 6 °, for example of the order of 3 ° in a direction of rotation said direct, and is for example between 2 ° and 8 °, for example of the order of 5 °, in a direction of rotation opposite, said retro direction, with respect to a rest position in which no torque is transmitted through the device. The rest position is illustrated in Figures 8 and 15 in particular.
    It is recalled that the direct direction corresponds to the case of operation in which torque is transmitted from the guide washers 16a, 16b to the hub 14. In certain operating phases, for example when the user abruptly removes his foot from the accelerator, a resistive torque is transmitted from the hub 14 to the guide washers 16a, 16b, which can cause a rotation in the retro direction.
    The application washer 63 further comprises recesses 72, 74, here eight in number, whose function will be better detailed after. Four of these recesses, namely the recesses referenced 72, comprise latching means 76 in the form of hooks or lugs.
    The applicator washer 63 further comprises an annular friction surface 78, extending radially, facing the first guide washer 16a and opposite the variable hysteresis washer 64.
    The second elastic washer 66 is mounted in abutment between the first guide washer 16a of the primary damper A1 and the radial surface 78 of the applicator washer 63. According to an embodiment not shown, the annular friction surface 78 comprises a metal part, for example a metal annular insert, fixed relative to the application washer 63, to reduce the wear of the application washer 63 in operation.
    The spring washer 66 is preferably of spring steel and is secured in rotation with the first guide washer 16a of the primary damper A1 by conventional means, for example by cooperation of tabs and complementary notches.
    The variable hysteresis washer 64 is made for example from a metal sheet, and comprises a substantially radial annular portion, from which eight lugs 80, 82 extend axially in the direction of the application washer 63 and from which four lugs 84 extend radially outwardly. The tabs 82 have notches 86. The tabs 80 are engaged in the recesses 74 and the tabs 82 are engaged in the recesses 72 so that the hooks 76 snap into the notches 86. The washers 63, 64 are thus fixed snap-fit to each other. The springs 25b belonging to the conditional activation damping means are housed with clearance between the tabs 84.
    Note that the variable hysteresis washer 64 has a relatively simple and robust structure in that it lacks wedge-shaped rims, so that its manufacture is relatively easy.
    A bearing washer 88, made for example of metal, is interposed axially between the annular portion of the variable hysteresis washer 64 and the inner periphery of the annular web 24.
    The second elastic washer 66 made of steel and the surface 78 of the applicator washer 63 form two complementary radial friction surfaces F3 (FIG. 1) intended to bear on one another so as to create a mixed friction plastic / steel type.
    Furthermore, the metal variable hysteresis washer 64, and the guide washer 16b, also made of metal, form two complementary radial friction surfaces F4 (FIG. 1) intended to bear one on the other .
    In addition, the variable hysteresis washer 64 and the bearing washer 88 form two complementary radial friction surfaces F5 (Figure 1) intended to bear on one another.
    In addition, the bearing washer 88 and the web 24 form two complementary radial friction surfaces F6 (Figure 1), intended to bear against one another. It will be noted that the washer 88 is made integral in rotation with the guide washer 16b, by means of tabs 89 mounted in slots of complementary shape to the guide washer 16b.
    It will also be noted that the assembly comprising the web 24, the guide washers 34a, 34b, the resilient members 43a, 43b, the washers 63, 64, and the washer 88 may form a pre-assembled module. It can thus facilitate the assembly of the clutch device.
    A third spring washer 92 is mounted in abutment between the first guide ring 16a of the primary damper A1 and the outer radial periphery of the first guide ring 34a of the pre-damper A2.
    The third spring washer 92 is secured in rotation with the guide washer 16A of the primary damper A1 by conventional means, for example by cooperation of radial tabs and complementary notches.
    The guide ring 34a of the pre-damper A2 and the third spring washer 92 define two complementary radial friction surfaces F7 (FIG. 1) intended to bear on each other.
    The device further comprises two friction washers 93, 94 and a fourth elastic washer 96 of axial compression, preferably of spring steel. Washers 93, 94, 96 are coaxial.
    The washer 93 is preferably made of steel and comprises a radial annular portion from which lugs 93a (FIG. 1) extend axially and are engaged in notches in the web 42 of the pre-damper A2 so as to perform a rotation coupling of the washer 93 and the web 42. The annular portion of the washer 93 further includes notches 93b at its outer periphery.
    The washer 94 is preferably made of plastic material, optionally reinforced with fibers. It comprises a radial annular portion from which pads 94a (Figure 1) extend axially so as to engage in the notches 93b of the washer 93. The two washers 93, 94 are thus coupled in rotation. one to another.
    The washer 93 and the fourth guide ring 34a form two complementary radial friction surfaces F8 (FIG. 1) intended to bear on each other.
    In addition, the washer 94 and the spring washer 96 form two complementary radial friction surfaces F9 (Figure 1), intended to bear against one another.
    The fourth spring washer 96 is mounted in abutment between the first guide washer 16a of the primary damper A1 and the washer 94.
    The fourth spring washer 96 is secured in rotation with the guide washer 16a of the primary damper A1 by conventional means, for example by cooperation of radial tabs and complementary notches.
    The main aspects of the operation of such a clutch device 10 will be described below.
    When the engine of the motor vehicle is operating at an idle speed, the primary damper A1 behaves like a rigid member because of the relatively high stiffness of its elastic members 26a, 26b, 28a, 28b. In this case, the torque provided by the crankshaft of the engine is directly transmitted from the friction disk 12 to the annular web 24 of the primary damper A1.
    The guide washers 34a, 34b being integral in rotation with the web 24 of the primary damper A1, the rotational torque is also transmitted to the guide rings 34a, 34b.
    The rotational torque is then transmitted from these guide rings 34a, 34b to the auxiliary web 42 of the pre-damper A2, and therefore to the hub 14, via the elastic members 43 which are then compressed.
    During this first phase of operation, friction is generated: - between the hub 14 and the bearing 18 at the friction surfaces F1, - between the hub 14 and the bearing 20, at the friction surfaces F2, - between the washer 93 and the guide washer 34a, at the friction surfaces F8, - between the spring washer 96 and the washer 94, at the friction surfaces F9.
    The corresponding friction surfaces are held in abutment by the axial compressive forces exerted by the spring washers 60, 96.
    By continuing the deflection of the web 24 relative to the hub 14, the circumferential clearance J1 between the internal toothing 23 of the web and the corresponding external toothing 15e of the hub 14 is overtaken, so that the web 24 and the hub 14 are coupled in rotation . From this moment begins a second phase of operation in which the pre-damper A2 no longer intervenes in the transmission of the torque which is directly transmitted from the web 24 of the primary damper A1 to the hub 14.
    Therefore, the torque is then transmitted from the friction disc 12 to the hub 14 via the primary damper A1.
    In this second phase of operation, the vibrations and irregularities of the torque are damped in a first step by the elastic members 26a, 26b with immediate activation of the primary damper A1 and by the friction generated: - between the hub 14 and the bearing 18 at the level of the friction surfaces F1, - between the hub 14 and the bearing 20, at the level of the friction surfaces F2, - between the web 24 and the washer 88, at the level of the friction surfaces F6, - between the elastic washer 92 and the guide washer 34a, at the level of the friction surfaces F7, between the spring washer 96 and the washer 94, at the friction surfaces F9.
    The corresponding friction surfaces are then held in abutment by the axial compressive forces exerted by the spring washers 60, 92 and 96.
    In this third phase of operation, the angular displacement between the guide washers 16a, 16b and the annular web 24 of the primary damper A1 exceeds the threshold angle of the primary damper A1. In this case, the vibrations and irregularities are damped by the elastic members 26a, 26b with immediate activation, by the conditional activation elastic members 28a, 28b of the primary damper A1, and by the friction generated: - between the hub 14 and the bearing 18 at the friction surfaces F1, - between the hub 14 and the bearing 20, at the friction surfaces F2, - between the web 24 and the washer 88, at the friction surfaces F6, - between the elastic washer 92 and the guide washer 34a, at the friction surfaces F7, - between the spring washer 96 and the washer 94, at the friction surfaces F9. between the variable hysteresis washer 64 and the guide washer 16b, at the level of the complementary friction surfaces F4, between the variable hysteresis washer 64 and the washer 88, at the level of the complementary friction surfaces F5, between the spring washer 66 and the application washer 63, at the level of the complementary friction surfaces F3.
    It will be noted that, in this third phase of operation, the pads 35a of the guide washer 34a bear against the corresponding lateral edges of the housings 70, so as to rotate the assembly formed by the application washer 63 and by the variable hysteresis washer 64. It is thus noted that, contrary to the prior art, the driving of said washers 63, 64 is not achieved using the tabs 84, which are relatively fragile.
    Furthermore, in this third phase of operation, the corresponding friction surfaces are held in abutment by the axial compressive forces exerted by the spring washers 60, 66, 92 and 96.
    Three damping stages are thus obtained, which are successively activated as a function of the angular displacement between the friction disk 12 and the hub 14.
    The hysteresis pairs generated during these different phases are different, in particular because of the number and the nature of the active friction surfaces.
    权利要求:
    Claims (15)
    [1" id="c-fr-0001]
    Torque transmission device (10), in particular for a motor vehicle, comprising a torque input element (12, 16a, 16b) intended to be coupled to a crankshaft and comprising a first and a second guide ring ( 16a, 16b), an annular web (24), a torque output member comprising a hub (14) for coupling to an input shaft of a gearbox, the web (24) being slidable along its axis (X) with respect to the hub (14), a primary damper (A1) arranged between the torque input member (12, 16a, 16b) and the web (24) and a secondary or secondary damper damper arranged between the web (24) and the torque output member (14), friction means capable of generating a hysteresis torque during the rotation of the web (24) with respect to the input element of torque (12, 16a, 16b), said friction means comprising an application washer (63) axially mounted t between the web (24) and the first guide ring (16a), a variable hysteresis ring (64) mounted axially between the second guide ring (16b) and the web (24), at least one elastic member tending urging the application washer (63) and / or the web (24) toward the variable hysteresis washer (64) so that said variable hysteresis washer (64) generates a hysteresis torque by friction, the variable hysteresis washer (64) and the application washer (63) being rotatably coupled to each other, characterized in that the pre-damper (A2) has at least one auxiliary guide washer (34a, 34b) coupled in rotation with the web (24), said auxiliary guide washer (34b) having a stop (35a) adapted to cooperate with a complementary abutment (70) of the application washer (63) so as to to perform a coupling in rotation of the web (24), the washer d variable hysteresis (64) and the application washer (63), when the deflection of the web (24) relative to the torque input member (12, 16a, 16b) exceeds a predetermined angular range and decoupling the web (24), on the one hand, and the variable hysteresis washer (64) and the application washer (63), on the other hand, when said deflection is located in said determined angular range.
    [2" id="c-fr-0002]
    2. Device (10) according to claim 1, characterized in that the pre-damper (A2) comprises a first and a second auxiliary guide washers (34a, 34b) coupled in rotation with the annular web (24), a veil auxiliary annulus (42) axially mounted between the auxiliary guide washers (34a, 34b) and rotatably coupled to the torque output member (14), and at least one resilient member (43) mounted between the auxiliary guide washers (34) (34a, 34b) and the auxiliary web (42) and adapted to oppose the rotation of the auxiliary guide washers (34a, 34b) relative to the auxiliary web (42).
    [3" id="c-fr-0003]
    3. Device (10) according to claim 1 or 2, characterized in that it comprises a first bearing (18) rotatably coupled to the first guide washer (16a) and a second bearing (20) coupled in rotation to the second guide ring (16b), the hub being held in abutment against the first bearing (18) and against the second bearing (20).
    [4" id="c-fr-0004]
    4. Device (10) according to claim 3, characterized in that the hub (14) is held in abutment against the first bearing (18) and against the second bearing (20) by at least a first elastic washer (60), mounted between one of the guide washers (16a, 16b) and one of said bearings (18, 20), and adapted to exert an axial force tending to press said bearing (18) on the hub (14).
    [5" id="c-fr-0005]
    5. Device (10) according to one of claims 1 to 4, characterized in that it comprises a second elastic washer (66) disposed axially between one of the guide washers (16a, 16b) and the washer of application (63), able to exert an axial force on the washer (63).
    [6" id="c-fr-0006]
    6. Device (10) according to one of claims 3 to 5, characterized in that the first and second guide rings (16a, 16b) are pivotally mounted around the hub (14), via the first and second bearings (18, 20),
    [7" id="c-fr-0007]
    7. Device (10) according to one of claims 1 to 6, characterized in that the application washer (63) comprises housings (70) in which are engaged, with an angular play, pads (35a) d at least one guide washer (34a) of the pre-damper (A2), so as to form the complementary abutments.
    [8" id="c-fr-0008]
    8. Device (10) according to one of claims 1 to 7, characterized in that a bearing washer (88) is interposed axially between the variable hysteresis washer (64) and the inner periphery of the annular web ( 24).
    [9" id="c-fr-0009]
    9. Device (10) according to claim 8, characterized in that the bearing washer (88) is rotatably secured to the second guide ring (16b) by means of tabs (89) of the washer. which are mounted in complementary shape of the second guiding washer (16b).
    [10" id="c-fr-0010]
    10. Device (10) according to one of claims 1 to 9, characterized in that a third elastic washer (92) is mounted in abutment between the first guide washer (16a) of the primary damper A1 and a washer guide (34a) of the pre-damper (A2).
    [11" id="c-fr-0011]
    11. Device (10) according to claim 10, characterized in that the third elastic washer (92) is secured in rotation with the first guide washer (16A) of the primary damper (A1).
    [12" id="c-fr-0012]
    12. Device (10) according to claim 2 and according to one of claims 3 to 11, characterized in that it comprises a first and a second friction rings (93, 94) coupled in rotation with the auxiliary web of the meadow shock absorber (A2).
    [13" id="c-fr-0013]
    13. Device (10) according to claim 12, characterized in that a fourth elastic washer (96) is mounted in abutment between the first guide washer (16a) of the primary damper (A1) and the second friction washer (94).
    [14" id="c-fr-0014]
    14. Device (10) according to claim 13, characterized in that said fourth spring washer (96) is secured in rotation with the first guide ring (16a).
    [15" id="c-fr-0015]
    15. Device (10) according to one of claims 1 to 14, characterized in that the primary damper (A1) comprises, on the one hand, damping means immediate activation, which are activated as soon as begins the angular displacement between the guide washers (16a, 16b) and the web (24), and on the other hand, so-called conditional activation damping means, which are activated here when the angular displacement between the guide washers (16a, 16b) and the web (24) exceeds a predetermined threshold angle from a rest position, said threshold angle of the primary damper (A1).
    类似技术:
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    同族专利:
    公开号 | 公开日
    EP3150881B1|2018-04-25|
    BR102016021085A2|2017-03-28|
    CN107023587B|2020-08-18|
    CN107023587A|2017-08-08|
    EP3150881A1|2017-04-05|
    FR3041402B1|2017-09-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR2918431A1|2007-07-04|2009-01-09|Valeo Embrayages|FRICTION CLUTCH EQUIPPED WITH A PRE-DAMPER COMPRISING FRICTION SYSTEMS HYSTERESIS AND DRAWER DEPENDENT|
    US3314512A|1965-07-02|1967-04-18|Borg Warner|Coupling device employing flexible hub assembly|
    JP3675644B2|1998-07-17|2005-07-27|株式会社エクセディ|Damper mechanism|
    FR2918432B1|2007-07-04|2009-09-25|Valeo Embrayages|FRICTION CLUTCH EQUIPPED WITH A PRE-DAMPER COMPRISING HYSTERESIS FRICTION SYSTEMS AND INDEPENDENT DRAWERS|
    CN202007859U|2011-03-30|2011-10-12|比亚迪股份有限公司|Torsion shock absorber and clutch cover assembly comprising torsion shock absorber|
    EP2850332B1|2012-05-14|2020-02-19|Clutch Industries Pty Ltd.|Friction clutch assembly|FR3064036B1|2017-03-17|2019-03-22|Valeo Embrayages|CLUTCH DISC WITH FRICTION WASHER|
    FR3071291B1|2017-09-18|2020-02-28|Valeo Embrayages|TORQUE TRANSMISSION DEVICE, TORSION SHOCK ABSORBER AND ASSOCIATED ASSEMBLY|
    FR3079580B1|2018-03-30|2020-09-18|Valeo Embrayages|TORSION DAMPING DEVICE WITH AXIAL GUIDED SPRING SEAT|
    CN108591363B|2018-04-28|2020-02-07|福建省汽车工业集团云度新能源汽车股份有限公司|Shock attenuation connection structure for oil-electricity hybrid vehicle|
    法律状态:
    2016-09-28| PLFP| Fee payment|Year of fee payment: 2 |
    2017-03-24| PLSC| Search report ready|Effective date: 20170324 |
    2017-09-29| PLFP| Fee payment|Year of fee payment: 3 |
    2018-09-28| PLFP| Fee payment|Year of fee payment: 4 |
    2019-09-30| PLFP| Fee payment|Year of fee payment: 5 |
    2020-09-30| PLFP| Fee payment|Year of fee payment: 6 |
    2021-09-30| PLFP| Fee payment|Year of fee payment: 7 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1558813A|FR3041402B1|2015-09-18|2015-09-18|TORQUE TRANSMISSION DEVICE, IN PARTICULAR FOR A MOTOR VEHICLE|FR1558813A| FR3041402B1|2015-09-18|2015-09-18|TORQUE TRANSMISSION DEVICE, IN PARTICULAR FOR A MOTOR VEHICLE|
    BR102016021085A| BR102016021085A2|2015-09-18|2016-09-13|torque transmission device, especially for automotive vehicles|
    EP16189143.7A| EP3150881B1|2015-09-18|2016-09-16|Torque transmission device, in particular for a motor vehicle|
    CN201610828640.0A| CN107023587B|2015-09-18|2016-09-18|Torque transmission device, in particular for a motor vehicle|
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